Automatic power transmitting mechanism



A ril 26, 1938. .1. E. PADGETT AUTOMATIC POWER TRANSMITTING MECHANISM;

Filed Dec. 19, 1934 7 Sheets-Sheet 1 April 26, 1938. J. E. PADGETT 2,115,212 I AUTOMATIC POWER TRANSMITTING MECHANISM v Filed Dec. 19, 1934 I '7 Sheets-Sheet 2 IIIIIIIIIIQI- April 26, 1938. J. E. PADGETT 2,115,212.

' AUTOMATIC POWER TRANSMITTING MECHANISM Filed Dec. 19, 1934 Y Sheets-Sheet 4 5154;, mmrwm SIT/Mum" April 26, 1938.

J. E. PADGETT AUTOMATIC POWER TRANSMITTING MECHANISM Filed Dec. 19, 1934 7 Sheets-Sheet 5 qlrm 3 mm Joseph E Paa'ycff JIMM/m April 26, 3 I J. E. PADGETT 2,115,212

cmuu sm Filed Dec. 19, 1934 7 Sheets-Sheet 6 Patented Apr. 25,1938

UNITED STATES PATENT OFFICE arisen AUTQ MATIO POWER TRANSMITTING MECH- ANISM Joseph 1;. Padgett, Toledo, Ohio- Application December'fl, 1934, Serial No. 758,327 I 4 Claims. (cl. 14-200) semi-automatic, or selective automatic in opera- -tion,,as it automatically effects a change in the constructions used. Prior transmissions of this torque multiplication when a reversal of drive occurs therein. Although transmissions of this general character have been heretofore proposed, they have not proved altogether satisfactory for several reasons. One of the defects of such prior transmissions, which are of. complex and expensive construction, is'that they are so designed that it is necessary .to decelerate the'engine to speeds below the speed of the driven shaft in order to effect the shift, with the result that-when the shift does occur, the vehicle must pick up the engine with the result that the vehicle loses considerable headway while this shift operation is being eflected. r v

The shift operation just described'is also defective because proper consideration has not been given the design of the parts of such prior trans- ,missions,'with the result that when the shift .occurs the vehicle is suddenly retarded in an undesirable manner. It has been proposed to remedy this defect of such prior transmissions by incorporating a clutch therein that would slip to some extent in one direction, but this resulted in complicated impractical structures, and did not fully cure the trouble because with such transmissions the loss of considerable headway was still involved in shifting. It was still necessary to wait a substantial period of time, during which no power. was transmitted, to allow the engine to decelerate to speeds below the speed of the driven shaft and effect the shift.

My improved transmission also embodies an auxiliary transmission, disposed in the drive line for affording. an emergency torque multiplication range, and although prior transmissions have been heretofore devised utilizing an arrangement of this general character, in such prior arrangements it is almost impossible to shift the amtiliary transmission unless the vehicle is at rest, because of synchronizing difficulties due to the general character which have been heretofore proposed have been complex and expensive mechanisms and they also possess the further serious disadvantage of being dimcult if not impossible to adjust when the parts become worn through use. a 7 V Prior automatic transmissions heretofore proa transmission having a selective auxiliary transposed, and which were ostensibly developed to simplify the control of automotive vehicles, have as a matter of fact been equipped with controls that are far more complex than those now used with conventional hand-shifted transmissions. 5

It is accordingly a major object of the present invention to devise a transmission which will automaticaliy shift and change the torque multiplication ratio between apriine mover and a load in response to a change in the driving relations of the parts in the transmission, without entailing any substantial loss of headway of the load, and

without imparting to the load a sudden forward driving or retarding impulse of any considerable magnitude.

It is a further major object 'of my invention to devise automatic transmissions that fully meet all of the operating requirements ofautomotive and similar drives, and yet that are'of low cost,

simple and compact design. permitting them to be readily installed in the space allotted to such units in automotive vehicles and the like.

A further important object of my invention is to devise, for use on automotive vehicles, or the like, a transmission that will drive the vehicle through a certain torque multiplication when the 25 vehicle is started, and that will automatically shift into a lower torque multiplication or higher gear ratio without a perceptible shock or impulse when the transmission is momentarily driven by the vehicle, and before the engine decelerates to speeds below the speed corresponding to the vehicle speed in the lower torque multiplication.

It is another object of my invention to devise mission so associated with it that the auxiliary transmission maybe readily shifted during any phase of operation, without synchronizing difllculties.

A further object of the invention is to devise a transmission having a forward-reverse gear train and a. uni-directional gear train disposed between a prime mover and a load, and to provide means for automatically preventing the unidirectional gear train from overrunning when the forward-reverse gear train is operating in reverse.

It is another object of this invention to provide a transmission of the character that automati cally shifts" in response .to changes in driving relations, with 'novel means for selectively preventing the transmission from responding to such changes.

portant, but more detailed transmission features that will hereinafter appear.

My invention further aims to design a transmission of the general character that automatically shifts when a reversal of drive occurs therein, through which the vehicle or other load will be smoothly picked up in a new gear ratio when the transmission shifts, irrespective of the manner in which the transmission is operated.

Another object of this invention is to devise a novel remote-control mechanism for actuating transmissions and the like.

A still further object of this invention is to devise an automatic clutch having means associated therewith that are constantly operable to transmit power from the driven to the driving member even when the clutch is disengaged, and yet which is incapable of transmitting power from the driving to the driven member.

I My invention also aims to provide selective or other transmissions with a novel device for iacilitating shifting the same into different gear ratios and reducing shifting noises to a minimum. It is another object of this invention to devise a transmission that normally will automatically shift into a higher gear when the direction of drive is reversed, and yet which may be operated to maintain the transmission in the higher gear at all times, irrespective of the direction of drive.

Further objects of my invention will become apparent as the description thereof proceeds in connection with the annexed drawings, and from the appended claims.

In the drawings:

Figure 1 is a longitudinal sectional view of the preferred form of my invention, and in order to clarify the illustration, the section through the upper part of the carrier has been taken at 90 from the section of the cover part thereof.

Figure 1A is a detailed sectional view of the knife edge assembly associated with the primary clutch throwout mechanism disclosed in Figure 1 of the drawings.

Figure 1B is a view partly in section and partly in elevation as seen when looking down on top of the structure Figure 1A.

Figure 2 is a fragmental detail view' of one of the holdback bolt assemblies employed in the form of my invention disclosed in Figure 1.

Figure 3 is a view taken substantially on line 3-4 of Figure l, and illustrates the overrunning clutch assembly utilized therewith.

Figure 4 is a view taken substantially on line 4-4 of Figure 1, and illustrates the pinion carrier lock mechanism.

Figure 5 is a view of the manual clutch and latching means therefor employed in the form of my invention shown in Figure 1.

Figure 6 is a view taken substantially on line 6-6 of Figure 1, and discloses the control mechanism for actuating the gear box thereof.

Figure 7 is a view partly in section and partly in elevation as seen when looking from the right of Figure 6, with certain of the parts thereof omitted for clarity of illustration.

Figure 7A is a fragmental View in section taken substantially on line 'IA-1A of Figure 4.

Figure 8 is a view in elevation illustrating the manual control assembly utilized with that part of my invention disclosed in Figure 6.

Figure 9 is a longitudinal sectional view of a modified form of secondary clutch which may be associated with the embodiment of my invention shown in Figure 1.

Figure 10 is a view in elevation of the manual control employed with the secondary clutch shown in Figure 9.

Figure 11 is a longitudinal sectional view, similar to Figure 1, of an alternate form of my invention.

Figure 11A is a sectional view taken on line ilA-I IA of Figure 11, and illustrating the overrunning clutch assembly employed therein.

Figure 12 is a sectional view taken substantially on line l2--i2 of Figure 11, and illustrates the actuating assembly for controlling the gear box thereof.

Figure 13 is a bottom elevational view of the gear box clutch sleeve disclosed in Figure 11.

Figure 14 is a fragmental elevational view as seen when looking in from the right of Figure 12, parts thereof being omitted for clarity of illustration.

Figure 15 is a view in elevation of the control assembly associated with the form of my invention disclosed in Figure 11, as seen when it is viewed from the opposite side thereof.

Figure 16 is a fragmentary elevational view of further parts of the control assembly associated with the form of my invention disclosed in Figure 11 as it appears when it is viewed from the near side of the transmission.

\ With continued reference to the drawings, wherein like reference characters designate like parts throughout the several views thereof, my novel power transmitting mechanism is enclosed in a housing denoted generally at i.

The mechanism, when broadly considered, consists of a low speed, or primary clutch which is adapted to initiate the drive through a'torque multiplying mechanism, a high speed or secondary clutch which is adapted to establish a direct drive between the prime mover and the load when the latter has been accelerated to snaredetermined speed, and an auxiliary gear box adapted to selectively provide a further amplification of the torque transmitted to the load. The description of the various parts will accordingly be divided into separate parts, so as to facilitate understanding the various phases of the invention. The primary clutch will be considered first.

' Primary clutch A driving shaft 3 is adapted to have rotational efforts applied to it by a suitabie prime mover in any desired manner, and in the present instance, it is shown as constituting the crank shaft of an internal combustion engine. The flanged end of shaft 3 is secured to a flywheel 4 by bolts 5, or in any other suitable manner. Bolts 5 extend through aligned apertures in the flywheel and the flange of shaft 3-, and have nuts turned thereon.

Shaft 3 is further provided with a bore 6 in which is carried a bearing assembly I for supporting the reduced end 8 of a shaft 9. The rear end of shaft 9 is adapted to be journalled in a bearing assembly that will be described hereinafter.

A hub H is splined upon shaft 9 and is provided with a flange l2. Operatively secured to flange l2, by means of rivets or the like, is a vibration dampener designated generally by reference character l3, which provides a resilient driving connection between hub II and a driven disc M. This vibration dampener is employed to F dampen out any torsional vibrations that may be set up in the crank shaft of the engine, and in viewof the fact that it forms no part of the present invention, it will not be further described.

Facings l5 and I 8 are secured to opposite sides acteristics to give the correct frictional gripping force, and at the same time has wearing qualities adapting it for this purpose. I prefer. however, to use the types of material which in practice have given very satisfactory results in automatic slipping drive and clutch mechanisms of the Powerflo type. One form of material, embodying colloidally associated copper particles and powdered graphite, is disclosed in co-pending 1111- plication Serial No. 685,603 filed August 1'7, 1933, and which is particularly suitable for use in the present mechanism. Frictional facings l5 and.

l 6 may be secured to disc l4 in any suitable manner; as for instance by rivets or the like, andthey,

along with disc M, will be hereinafter referred to as a driven member.

Facing i5, secured to disc l4, cooperates with the fiat driving face of flywheel 4 and is adapted to be frictionally driven thereby. Facing 15, cooperates with a plate 23 which will be hereinafter termed the automatic plate.

Secured to the flywheel. rim portion in any suitable manner as for example by bolts 18 (Figure 2) is a cover member l9 which carries on its. inner wall driving lugs or key members 2| which are preferably three in number and symmetrically arranged about the inside of the cover. The keymembers are received in and cooperate, with the walls of recess 22 formed in automatic plate 23. Y

Disposed parallel to plate 23 is a plate 24, and it will be hereinafter referred to as a reaction plate, because it takes the reaction of a speed responsive mechanism in a manner to be presently described. Reaction plate 24 is driven by automatic plate 23 through the medium of a plurality of cap screws 21. Referring particularly to Figure 2, each cap screw 21 is provided. with a reduced end 28 that is threaded in automatic plate 23, and the thread employed is preferably of the Dardelet or other self-locking type so as to-prevent the cap screws from working loose in operation. Cap screws 21 extend through, and lie in the path of driving engagement with the walls of recesses 29 formed by reaction plate 23, and are encircled by washers 3| and 'compres-;"

sion spring 32. Spring 32 acts against the head of bolt 21 and reacts against the plate 24 to thereby urge the automatic and reaction plates toward each other at all times, and they will be hereinafter referred to as holdback springs. The holdback spring assemblies are preferably symmetrically disposed in pairs about the periphery of the plate, and-in the present instance six are employed. Theuholdback spring assemblies accordingly establish a driving connection between the automatic and reaction plates, and at the same time resiliently urge them toward each other.

Reaction spring. 24 is normally urged toward the flywheel by a plurality of compression springs actuated away from each other by .any suitable speed-responsive mechanism, to produce clutch engagement, but in the present instance it preferably takes the form of a centrifugally operable mechanism. Preferably three weight levers 4l, having integrally formed heads 42,'are symmetrically arranged between the pairs of pressure springs 35, and have their heads 42 received in rectangular recesses 43 formed in automatic plate 23.

Each lever 4i isprovided with a pair of threaded portions 44 to which is secured a weight element 45 by means of nuts 41.

Levers 4| are of substantial width and extend through recesses 48 formed. in reaction plate 24. Heads 42 are provided with flat faces that normally abut the bottoms of recesses 43 when the driving shaft is operating at, or below-idling speed, and by the term idling speed, I mean the particularly desired automatic uncoupling or disengaging speed of shaft 9, and if an internal combustion engine is employed as the prime mover, the idling speed will lie in the neighborhood of four hundred to five hundred revolutions per minute.

Heads 42 are also provided with reaction faces 49 which abut the face of reaction plate 24 at all times, and are designedfor fulcruming engagement therewith during operation of thelevers 4! are clamped between plates 23 and 24 under the influence of springs 35 acting against plate 24 and cap screws 21, and plate 24 is held in the position shown, against the action of. springs 35 by means of a throwout mechanism now to be described.

Extending through apertures 5i formed in reaction plate 24, and preferably symmetrically disposed between the weight assemblies, are a plurality (three) of bolts 52 provided with knurled portions which serve to prevent rotationof the bolts with respect to the reaction plate. Referring in particular to Figures 1A and 13, it will be seen that bolts 52 are provided with slots 56 in the end of the bolts remote from the reaction plate. The exterior of each bolt in this region is threaded as indicated at 51 and is adapted to have threaded thereon a castle nut 58 which may be locked in position uponv the bolt by peening the nut within the slot formed in the bolt. in turn is adapted to bear against the cross head 60 of a T-shaped member 5|, formed with a stem 52. As will be seen from Figures 1A and 1B, stem 52 is designed to lie within slot 56 adjacent the castle nut 58. Cross head 60 of the T-shaped member is adapted to extend through and outwardly beyond the confines of bolt 52 as shown Castle nut 58 abutsa washer 59 which in Figure 1B. The cross head 60 is relieved as 64 serves a purpose to be presently disclosed. Althoughnot shown in the drawings, due to difliculties of illustration, a slight clearance exists between the T-shaped member and the walls of the slot formed in bolt 52, for a reason to presently appear.

Mounted on pins 1| carried by brackets I2 secured to a depressed portion "pf the cover member 18 is a plurality (three) of clutchfingers 14 each of which at its upper end is provided with bifurcated portions 15, which lie one on each side of bolt 52. One face of each of the bifurcated portions is recessed as shown at I8 and is adapted for contact with knife edge 84 of the T-shaped member. The other edge of each bifurcated portion is rounded as indicated at 11 and is adapted to abut a washer 18 positioned on bolt 52 and spaced from reaction plate 24 by means of a light compression spring I8. Bifurcated portions 15 of the clutch lever are adapted through the T member SI and castle nut 58 to cause movement of reaction plate 24 toward or away from the flywheel 4 and washer 18 is designed to retract and hold clutch fingers 14 against rattling when they are not under the influence of springs 85.

Bolts 52 and nuts 58 are adapted to partially extend through apertures 8| formed in cover member l8, and the apertures are preferably of a size sufiicient to allow a wrench or the like to be applied to nut 58 for adjustment purposes.

Throwout fingers 14 and throwout bolts 52 which are symmetrically disposed about the periphery of the reaction plate are staggered with respect to the centrifugal weight assemblies, and in the present instance three throwout fingers and bolts are employed.

Movement of the inner ends of fingers 14 to the left in Figure 1, through the intermediary of bolts 52, causes actuation of plate 24 away from the flywheel against the action of springs 85 and this in turn produces similar movement of plate 28 because the holdback assemblies hold the two plates in unitary relationship at all times. Conversely, movement of the inner ends of fingers 14 to the right as seen in Figure 1 allows movement of the automatic and reaction plates as a unit toward the flywheel under the influence of springs 85.

Rotation of the throwout fingers in the manner just described is efiective to cause reciprocation of throwout bolts 52 in a smooth and even manner by virtue of the fact that each knife edge 58 is at all times in line contact along the same line with recess 85 of its washer 58,- and each knife edge 64 is at all times in contact along the same line with recess 18 of its throwout finger. Constant line contact between each knife edge 88 and each washer 58 is insured since neitherthe knife edge nor the washer undergo any vertical displacement. Constant line contact between knife edge 84 and recess 18 of the throwout finger is insured since recess 18 undergoes only a slight vertical displacement of approximately .004 inch during rotation of the throwout finger, and knife edge 84 is allowed to undergo a similar vertical displacement by virtue of the slight clearance previously described existing between the T member 58 and the walls of slot 55 of bolt 52.

With the throwout levers and bolts disposed in automatic position" as seen in Figure 1, line contact between knife edge 84 and the throwout lever exists in a perpendicular plane passing through the axis of pin II. If the throwout fingers are now rotated in a counter-clockwise direction about pin II into conventionally engaged position, or are rotated in a clockwise direction about pin H into completely released position, the line of contact existing between knife edge 84 and recess 18 of the throwout finger will be rotated about pin II as a center either to the left or the right of the automatic position. The angular displacement which the line of contact undergoes in the transition from automatic position to "conventionally engaged" position is substantially equal in magnitude to the angular displacement occurring in the transition from automatic po-' sition to "completely released" position and differs only in the direction in which such displacement takes place with respect to automatic position.

It will be appreciated that when the line of contact between knife edge 84 and the throwout lever undergoes angular displacement from automatic position into either of the two positions above described, the line of contact suffers a displacement whichmay be resolved into horizontal and vertical components. The horizontal component of such displacement is effective to cause reciprocation 'of throwout bolts 52, and such horizontal component comprises by far the major part of the resultant displacement which occurs. The vertical component of displacement is but very slight, and as previously described is effective to cause the T-shaped member to rock slightly within slot 55 of bolt 52 in effect comprising lost motion. It is thus seen that even minute rocking motion of the throwout fingers is translated into an almost identically equal linear motion of the throwout bolts with substantially no friction as only a slight loss of motion occurs due to the rocking of the T-shaped member within the throwout bolt slots.

Actuation of fingers I4 is effected by means of a throwout assembly that will now be described. Cooperating with curved faces" 83 formed on fingers I4 is the fiat face of a ball race 84, which cooperates with anti-friction balls 85 disposed between race 84 and a cooperating ball race 86. Ball races 84 and 88 are held in assembled relation with respect to each other by means of a combined retainer and reservoir defining member 81. The bearing assembly is preferably packed with lubricant during assembly. Ball race 88 is rigidly mounted upon a sleeve 88 which is adapted for axial movement on a sleeve 18 mounted concentrically with respect to shaft 8 in a manner to be presently set forth.

A sealing member 88 is secured to sleeve 88 and frictionally cooperates with ball race 84 so as to retain the lubricant in the bearing. Sleeve 88 is provided with lugs 88 which cooperate with throwout fingers 84 rigidly carried by a throwout shaft 85. Shaft 85 is preferably journalled in, and extends outwardly of clutch housing I, and is adapted to be actuated by mechanism to be hereinafter described.

Although I have disclosed a specific throwout assembly in connection with my invention, it is to be understood that any suitable throwout mechanism having a face that is substantially normal to the clutch axis for cooperating with the inner ends of fingers I4 may be employed if desired, and a thoroughly practical mechanism ob tained.

Shaft 85 is preferably adjustably held by any suitable mechanism in such a position that the throwout bearing assembly will hold the parts in the positions in which they are shown in Figure 1 when driving shaft 8 is stationary or is operating at or below a predetermined'idling speed of the upper end of lever latching edge or portion I09 .in Figure 5.

the prime mover'utilised therewith when it is desired to obtain normal, or speed-responsive clutch operation. Under these conditions, a clearance exists between the plates and there is accordingly no driving connection between shafts 3 and Any suitable latch in may be associated with shaft OI or the. clutch pedal for holding shaft 95 in the position shown in Figure l, but I preferably employ the mechanism disclosed As seen in this figure, shaft 95 extends outwardly from housing" I. A clutch pedal Ill provided with a split hub II! is mounted for. rotation with shaft 85 by means of a bolt I03 which rigidly clamps split huh II! to the shaft. -Also mounted for rotation with shaft 95 is a lever Ill which is thereto keyed. A link IDS is secured to II by means of apin 106. Link I05, provided with a riding face I" and a latching face ll'l, extends through an aperture I" located in, and cooperates with of aplate I I0 secured to the flywheel housing inany suitable manner. Plate H0 is provided with an apertured finger ill to which a tension spring 2 is secured, the spring at its other.end being secured to an'apertured member Ill which is swiveled on a pin ill carried by latch member I05. Spring 2 tends to hold link I05 in contact with latch portion It! at all times. An actuating wire 5 extends through an aperture in pin |H an d is securedtherein in any suitable manner. Wire 5 extends upwardly and is encased in a flexible housing member Ill, which terminates short of the latch assembly so that movement of member II! will not kink wire I [5. Wire H5 and housing Ill constitutethe well known Bowden wire structure which is led up to the vehicle dashboard H8 and is thereto secured in any suitable manner. Wire 5 adjacent the dashboard is provided with a knob 9 which may be withdrawn to lift latch member I05 with its latching face I01 clear of latch portion ll! of the bracket ii, to effect engagement of the clutch ,independently of centrifugal action as will now be set forth.

The parts are shown in Figure 5 as they appear when clutch pedal III .is latched against rotation by means of link I05 and bracket ill. When the parts are held in this position the throwout mechanism assumes'the position shown in Figure 1, and if the engine is operating at idling speed, the clutch will be disengaged as shown in this figure.

The parts are normally held in this position when control knob IIQ outwardly away as air automatic clutch, be hereinafter termed the clutch is being utilized and it will accordingly automatic position.

Shaft 95 may be released to allow rotation thereof and reciprocation of the throwout bearing assembly for causing manual engagement or disengagement of the primary clutch by drawinfl from the vehicle dashboard. Such operation lifts link ill andits latching face out of engagement with latching bracket 1 II to allow springs to force plates 23 and 24 to the left as a unit, which brings plate fl into engagement with the driven member. This results in movement of the throwout assembly to the .right and effects rotation of shaft .5. i

The parts may then be restored to automatic position by manually de chitch pedal Ill and retracting knob I". The primary clutch maybeatanytime,atthewillofthe operator by d the clutch pedal to its 5 miles: extent. During the disenga in operationthe-riding face'ofiatch lllridesupon edge lllof'plate-lil.

Manualactimtbnoftheclutchpedelforcontrollingtheprimaryclutchiseaentialaswillbe hereinafter pointed out in connection with the operation of the transmission.

Automatic cperationpj primary clutch Acceleration of shaft 3 slightly above the idling speed of the prime mover does not cause actuation of the weights because springs 32 hold them in check. As driving shaft 3, and flywheel l are accelerated to a speed idling speed, which is determined by the strength of springs 32, the mass of weights 4!, the proportions of the parts. and other factors, weights 6 gradually swing or rock outwardly about their knife-edges II as axes in response to centrifugal force. As this occurs, reaction faces 4! of heads 42 fulcrum and slide on the face of plate 2|, and knife edges II, by virtue of their engagement and fulcruming action upon the flat bottom surfaces of recesses 43 located in automatic plate 23, force the automatic plate away from reaction plate 24 32, and into engagement with facing I of disc I, thus causing disc ll to move axially and bring the facing I! thereof into contact with the flywheel. I

Movement of automatic plate 21 away from reaction member 24 is opposed by holdback springs 32, and therefore weights II are held under ccntrol. Holdback springs 32, therefore, in addition to predetermining the speed of the mechanism at which automatic engaging operation is initiateiexert a steadying influence upon the clutch After the driven member is thus frictionally clamped or gripped between automatic plate 23 and flywheel I movement of plate 23 issubstantially arrested and further rocking movement of weights 4, in response'to a further increase in centrifugal force, causes faces" of heads 42 to force reaction plate 21 away from the flywheel against the action of springs 35. Movement of plate 24 in this manner causes pressureto slowly build up in springs II and a corresponding pressure is built up between the edges SI of heads 42 and the bottoms of the recesses in automatic plate 2;. This action causes the plate pressure to build up comparatively slowly, with the result that the clutch smoothly picks up shaft 9.

When shaft I and flywheel 4 attain a predetermined speed the plate pressure builds up sufficiently to establish a non-slipping drive between shafts l and I, This speed is determined by the magnitude of the torque transmitted by the clutch, as under heavy loads, the speed will be higher than that required to establish a non-slipping drive when the load is light. When a still higher predetermined speed is attained, weights 4. rock out into contact with flanges formed on With continued reference to Figure 1, housing lisjoined at its rear end toahousing III which against the action of holdback springs encloses the rear portion of the automatic transmission, and is secured thereto in any suitable manner as for example by bolts I29. Sleeve 18, which supports the throwout bearing assembly of the primary clutch, is at its rear end provided with a flange I3I which is secured to housing I28 in any suitable manner as for example by means of bolts I32. Housing I28 is provided with inwardly extending partition forming walls I34 which are adapted to accommodate a ball bearing assembly I35 designed to support an enlarged portion I36 of shaft 6.

A snap ring I36 is designed to be accommodated within a groove formed in the outer race of ball bearing assembly I35, and the outer circumferential portion of the snap ring is accommodated between the flange I3I of sleeve 16 and the partition forming wall I34. The outer race of bearing assembly I35 is thus retained in position with respect to the transmission housing by the action of split ring I38 and further by the abutting action of flange I3I which overlaps the outer bearing race. Received in a groove formed in enlarged portion I36 of shaft 9 adjacent the inner race of ball bearing assembly I35 is a snap ring I39. The inner race of the ball bearingassembly is thus maintained in proper axial position upon shaft 9 by the action of the split ring and the enlarged portion I36 of shaft 9.

The portion of shaft 9 which extends into housing I26 is enlarged and provided with external teeth I42 and internal teeth I 43.

Enlarged portion I 36 of shaft 9 is provided with a bore I44, designed to accommodate the reduced end I45 of a shaft I46; Reduced portion I45 is journalled in bearings I41 which are adapted to receive lubrication from bearing I35 by means of an oil groove I46 formed in portion I36 of shaft 9. The rear end-of shaft I46 is supported in a manner to be presently described. Shaft I46 is provided with splines I5I, and bearings I41 are adapted to be positioned away from the splines by means of a spacer ring I52.

Rotatably mounted upon the rear portion of splines I 5I is a hub I53, provided with external teeth I54, and having a forward extension I55 provided with internal teeth I56. The forward wall of hub I53 is adapted to abut a collar I51 mounted on splines I5I and which in turn abuts a snap ring I58 accommodated within a groove formed in the splines, the hub I53 in this manner being prevented from displacement in a forward direction on shaft I46.

Splined on shaft- I46, between hub I53 and the expanded portion I of shaft 9 is a sliding clutch I6I provided with a flange I62 having an enlarged groove I63 for receiving the fingers of a shifter fork to be presently described. The forward portion of sliding clutch I6I is provided with external teeth I64 and the rear portion thereof is provided with external teeth I65, the teeth I64 being adapted to mesh with internal teeth I43 formed on expanded portion I of shaft 9, and

the teeth I65 being adapted to mesh with the internal teeth I66 formed on hub I53. With the parts disposed in the position shown in Figure 1, sliding clutch I6I is disposed in its neutral position, neither teeth I64 nor I65 cooperating with the internal teeth just described.

External teeth I42 formed on the expanded portion I of shaft 9 are adapted to mesh with teeth I68 formed on a cluster gear member I69, which is also provided with teeth "I adapted to mesh with external teeth I64 formed on hub I63. Member I69, to the rear of teeth "I, is provided with further teeth I13 for a purpose that will presently appear. Member I 69 is journalled by means of bushings I14 and I15 upona counter shaft I16 disposed parallel to shaft I46 and at its forward end received in partition forming wall I34 of housing I28, its rear end being secured against rotation in a manner to be presently described. The forward end of collar I69 is spaced from partition forming wall I34 by means of a thrust washer I16.

Keyed to shaft I46to the rear of splines I5I is a gear I6I provided with external teeth I82 which lie in the plane of teeth I13 formed on collar I66 and are adapted to be geared thereto by means of an idler reverse gear to be presently described. Gear I8I is spaced from hub I 53 on shaft I46 by means of thrust washer I83, and is thus prevented from displacement in a forward direction. The rear face of gear I8I abuts an enlarged portion I84 of shaft I46, which prevents displacement of gear I M rearwardly. Portion I94. of shaft I46 is journalled in a ball bearing assembly I85 received within a partition forming wall I66 which extends inwardly from housing 26. The inner race of bearing I85 is retained in positionby means of a snap ring I81 accommodated in a groove formed within enlarged portion I84 of shaft I46 and an enlarged portion I68 of shaft I46. The outer race of bearing I85 is retained in position by means of a snap ring I69 received in a groove in the outer bearing race, and a plate member I9I, which is secured to the partition forming wall in any suitable manner, as for example by bolts I92 and which extends inwardly into overlapping relation with the outer race. The outer portion of plate I9I extends into a recess I93 provided in the rear portion of shaft I16 previously described and is effective in this manner to prevent rotation of said shaft. Concentric about shaft I16 and lying against partition forming wall I86, is thrust washer I94 which is adapted to space collar I69 from the partition forming wall.

From the structure thus far described, it will be readily appreciated that when shaft 9 rotates external teeth I42 formed thereon will drive gear I68 to cause rotation of member I69 about stationary shaft I16. Rotation of member I 69 is accordingly effective to produce rotation of teeth I thereon formed which mesh with teeth I 54 and thereby cause rotation of hub I53. Thus any rotation of shaft 9 is effective to cause simultaneous rotation of collar I69 and hub I53.

With the parts disposed in the position shown in Figure 1, rotation of the elements in the manner just described is ineffective to cause rotation of shaft I46, due to the fact that hub I53 is freely mounted upon shaft I46. However, should sliding clutch I6I be reciprocated in a forward direction so as to bring external teeth I 64 thereon formed into meshing engagement with teeth I43 formed on shaft 9, any rotation of shaft 9 would be effective to cause rotation of shaft I46 since teeth I43 and I 64 would act in effect as keys to lock shafts 9 and I46 for unitary rotation. During such operation, collar I69, of course, rotates and causes hub I53 to merely "idle" about shaft I46, as there is no driving connection between hub I63 and shaft I46.

If, however, with the parts disclosed in the positions disclosed in Figure 1, sliding clutch I6I is reciprocated rearwardly to bring external teeth I66 thereon into meshing engagement with internal teeth I66 formed on hub I63, rotation of shaft 9, by means of teeth I42 and I68, and in turn through the medium of teeth In and m.

will be effective to cause rotation 'of hub I63' through a speed reduction gear ratio. As hub I63 is effectively keyed to shaft I46 by means of teeth I66, I66 and splines I6I, any rotation of the hub is effective to transmit torque to shaft I46. Thus, under these conditions, rotation of shaft 6 produces rotation of shaft I46 and torque transmitted to shaft I46 is amplified since gear I42 is ofiess diameter than gear I66 and gear I'll is of less diameter than gear I64.

Although I have illustrated a gear box having a single forward gear reduction, and I prefer to use this arrangement, it is to be understood that if desired a further set of gears may be provided to give either a further gear reduction or an overdrive ratio, without departing from the spirit of my invention.

In either of the two selected operations just described, which are effective to cause simulta-- neous rotation of shaft I46 with shaft 6, it is seen that shaft I46 rotates in the same direction as shaft 9. If, however, it is desired to cause shaft I46 to rotate ina direction the reverse of the direction in which shaft 6 is rotating, this may be accomplished through the medium of collar I68 and gear I6I, which may be selectively caused to rotate simultaneously by means of a reverse idler gear, to mechanism for actuating sliding clutch I6I will now be described together with the reverse shifter mechanism and controls therefor.

with continued reference to Figure 1, and with reference to Figures 6 and '1, it will be seen that sleeve I6I is adapted for cooperation with a shifter fork 20I provided with fingers 262, which are disposed within groove I63 formed in sliding clutch I6I'. Shifter fork 2" is provided with a hub 203 which is adapted, by means of a set screw 204, to be rigidly secured to a shaft 206. The end of shaft 206 disposed toward the forward end of the transmission, is adapted to reciprocate within a bore 261 formed in partition wall I64 of transmission housing I26. The end of shaft 206 disposed toward the rear of the transmission is adapted to reciprocate within a bore 208 formed in a boss 266 on partition wall I66. Hub 203 of the shifter fork is provided with an extension 2, which at its upperextremity is ,formed into a gear rack 2I2.

Shaft 266 is adapted to be selectively retained in its selected longitudinal positions with respect to the transmission housing by means of a ball detent 2 located within a bore no formed in an extension 2" integral with transmission housing I26. Ball 2I4 is urged by a spring 2I5 into any one of three longitudinally spaced depressions 2I3 formed on shaft 206. The depressions. correspond to direct drive, neutral and geared drive.

In Figure 6, gears I3I, I13 and a reverse gear presently to be described are indicated for clarity of illustration in phantom lines, to show their position with respect to each other, although the gears do not actually lie in the plane of the illustration, but are located in fact between the observer and the plane of the illustration.

Positioned parallel to shaft I46 and I16, and disposed in the same horizontal plane with shaft I16 is a shaft 22I having its forward end supported in a web 226 extending inwardly from housing I26 and at its rear end supported in' a manner similar to countershaft I16, with its rear end locked against rotation in partition waif I86. Mounted for rotation and reciprocation on be presently described. The shifter ment with said gears.

shaft 22I is a sliding clutch 222 comprising a collar 223 and a gear 224. This gear will hereinafter be termed the reverse idler gear. Reverse clutch 222 is mounted for reciprocation on reverse shaft 22I by means of a bushing 226. Gooperating with collar 223 of the reverse gear is a shifter fork 226 provided with fingers v 221. Shifter fork 226 is provided with a hub 226, which is rigidly mounted for movement with a shaft 229 by means of a set screw 23I-, which is held in set position by means of a wire 232 extending about a projection 233 formed on hub 226. Projection 222 extends upward In parallel relation to projection2II of hub 203, and terminates in a gear rack 234,-which is disposed in the same horizontal plane as gear rack 2I2. Shaft 226, as seen in Figure '1, is at its forward end adapted to re ciprocate within a bore 226 formed in partition wall I34 and at its rear end is-adapted for reciprocation in a bore 236 formed inboss 209 of partition wall I66. Shafts" 228 and mounted for similar reciprocation with respect to transmission housing I26. v

Shaft 228 is adapted to be selectively positioned with respect to the transmission housing by means of a ball detent 231 located in a bore 238 formed in extension 2" previously described, and

is urgedby means of a light compression spring two depressions corresponding respectively to neutral and reverse position. From the structure thus far developed, it will be apparent that selective positioning of sliding clutch I6I may be effected by lateral displacement of gear rack 2 I2, which by virtue of its rigid connection with shaft 206, causes displacement of the, shaft into selected position where it is yieldingly maintained through the medium of ball detent 2I4.

As will be readily appreciated from an inspection of Figure l, sliding clutch I6I may be disposed in any of 'three positions. With the parts disposed as shown in Figure 1, the clutch is disposed in what will be known as "neutral position, while if the clutch be shifted until teeth I64 thereof mesh with teeth I43 of shaft 6, it will be disposed in what-will be known as "high position, and if the clutch be disposed with teeth I65 thereof in meshed engagement with teeth I66 of 206 are thus hub I63, it will be disposed in'what will be.

the three selected positions.

Referring now to the mechanism for establishing reverse drive of shaft I46, it will be appreciated that reciprocation of the reverse clutch 222 may be effected by lateral displacement of gear rack 234 and shaft 226 rigidly assembled therewith. Thus it is possible to bring reverse gear 224 into meshing engagement with gears I13 and I62 or to bring gear 224 out of' engage- It will therefore be appreciatedthat there are only'two selective positions for the reverse sliding clutch 222, and in consequence it is necessary to provide only two depressions 2 in shaft 220 in order that detent 231 may retain shaft 226 in either of its selected positions.

With reverse clutch 222 disposed in the position disclosed in Figure 1, the clutch will be said to be in its "neutral" position. However, should the collar 222 be disposed so as to bring gear 224 into engagement positively with gears I13 and I82, the reverse collar 222 will be said to be disclosed in its positive position.

From the reverse structure thus far described, it will be readily apparent that if sliding clutch I6! be disposed in neutral position, that is the position indicated in Figure l, and the reverse sliding clutch 222 be disposed in its positive position, rotation of shaft 9 is effective through teeth I42 and IE8 to cause rotation of collar I89 in a reverse direction and this collar, by means of teeth I13 and reverse gear 224 is effective to cause rotation of the reverse idler gear in the same direction as shaft 9 is rotating. Rotation of gear 224 in this direction is effective through teeth I82 to cause rotation of gear I 8| in a reverse direction with respect to shaft 9 and, as gear l8I is keyed to shaft I46, such rotation of gear I8I will be effective to cause shaft I46 to rotate in a reverse direction with respect to shaft 9. It will thus be appreciated that by proper manipulation of gear racks H2 and 234, shaft 9 may be made to cause shaft I46 to rotate in a direction imparting reverse drive to the wheels of the vehicle.

Actuation of gear racks H2 and 234 in the manner just described is efiected by means of a segmental pinion gear 245 provided with teeth 246, which by means of a pin 241 is secured on the reduced end of a shaft 248. Shaft 248 is adapted to be reciprocated and rotated within a bore 249 formed in a cylindrical housing ZSI. Shaft 248 and gear segment 245 are urged to the left as seen in Figure 6 by means of a spring 252, disposed within bore 249, and which at one end bears against a shoulder 253 formed on cylindrical housing 25I and at its other end bears against a shoulder formed on shaft 248.

Cylindrical housing 252 is integrally formed with a cover plate 254 which is adapted to be secured to bosses 256 formed on housing I28 in any suitable manner as for example by bolts 251 or the like. Cover 254 is spaced from bosses 256 by means of a gasket member 258. It will thus be apparent that plate cover 254 is elfective to close aperture 268 formed within the transmission housing I28. However, by the simple expedient of removing bolts 251 and withdrawing cover plate 254. from the transmission housing, opening 268 will be exposed, and access may be had therethrough to the high and low shifter mechanism or to the reverse shifter mechanism previously described for adjustment or servicing.

Cylindrical housing 25I adjacent its end remote from transmission housing 28 is enlarged to form a casing member, indicated at 28I. The reduced end 262 of shaft 248 extends into the casing 26I, and by means of a pin 263, a sector gear 284 is secured onto the reduced shaft end. Sector gear 284, having a gear track 285, is provided with a flange 286 which lies adjacent one side of the gear rack. The other side of the gear rack is enclosed by a plate member 281 which is secured to sector member 284 in any suitable manner. Plate member 281 extends below the reduced end 262 of shaft 248 as seen at 288 and is provided with an arcuately formed recess 288.

A boss 215 is formed on the inside of casing 258 and held there-against is a disc member 218 which is retained in place by means of a bolt 211 having a nut 218 threaded thereon.

With the parts disposed in the position shown in Figure 8, it will be appreciated that rotation of sector member 284 will be effective to cause rotation of shaft 248, to which the sector member is secured, and segmental gear 245. Such rotation of gear 245 when teeth 246 and 2 I2 are in meshing engagement as shown in Figure 6 is effective to cause displacement of the shifter fork 28I into its various operative positions in the manner previously described. Should it be desired however to effect displacement of the reverse shifter fork 226, it is only necessary to cause lateral displacement of shaft 248 to the right (as shown in Figure 6) until teeth 246 of gear 245 are meshed with gear rack 234. Rotation of shaft 248 under such conditions is accordingly effective to cause selective displacement of reverse shifter fork'226. It will be observed that under ordinary conditions gear 245 is urged to the left (as seen in Figure 6) by virtue of the fact that compression spring 252 constantly tends to displace shaft 248 to the left.

Rotation and reciprocation of shaft 248 within bore 249 in the manner just described may be effected by means of sector gear 264 in a manner to be now described.

To housing section 26I is secured a mating section 28I adapted to house the assembly for actuating gear sector 264 and secured to section 26I in any suitable manner, as for example by means of cap screws 282 or the like. Extending inwardly from the wall of section 28I is a longitudinal boss 283 having a bore 284 adapted to accommodate, for reciprocation and rotation therein, a cylindrical rack member 285 on which are formed rack teeth 286 designed for meshing engagement with the teeth of sector gear 268.

One end of housing 26I is provided with an opening 281 to facilitate accessto the interior of the housing during manufacture, and this opening is adapted to be closed by means of a cover 288 which is secured in place within the opening.

Rigidly secured to one end of the cylindrical gear rack, by means of a recessed soldered connection, is a control cable 298 which enters housing 28I by way of a sheath anchoring assembly 29!. Control cable 298 is specially constructed so that it possesses substantially no torsional deflection under the loads to which it is subjected, and as cables of this character are known in the art, it will not be further described. Control cable 288 enters a sheath 293 and is led up to the vehicle dash-board. Adjacent the vehicle dashboard, the cable is rigily connected to a control knob 294. Control knob 294 is connected to a plunger 295, to which cable 293 is secured in a manner similar to its connection to rack 285, and plunger .285 is mounted for reciprocation and rocking movement in a bracket 296. The latter is connected to the vehicle dash 291 by means of a resilient bushing 298, so as to prevent transmission vibrations from being communicated to the dash instruments, 8. pin 299 connected to plunger 285 and working in an enlarged slot in bracket 288 is operable to prevent excessive strains being set up in cable 298 through improper actuation of knob 284. Tube 283 extends into bracket 296 and is adjustably related thereto by means of a nut and screw assembly 888, for securing the proper working length of the cable after the device has been installed in the vehicle.

Control knob 284 may be either rotated upon manual twisting thereof by the vehicle operator or may be reciprocated toward and away from the vehicle dash-board and such actuation of the knob is effective, through the medium of control wire 288, to cause corresponding rotation or reciprocation of cylindrical rack 285 within bore 284.

Rotation of cylindrical rack 285 within its bore under such conditions the elements cooperate asa simple rack and pinion fortranslating linea motion into rotary motion. v v

Rotation and reciprocation'of cylindrical rack 295 in the manner just described is thus effective through the medium of sector gear 264 to cause corresponding rotation and reciprocation of shaft 248 with resulting actuation of the control shafts 286 or 229 in the gear box and selective conditioning of the latter for transmission of torque therethrough. Thus it will be appreciated that conditioning of the gear box is at all times under the Y complete control of the vehicle operator who may at will selectively actuate knob 294 on the vehicle dash-board for any condition of torque transmission through the gear box.

With the parts ofthe mechanism disposed in the position shown in Figures 6 and 8, reciprocation of shaft 248 within bore 249 may be readily effected. It will be appreciated, however, that if sector member 264 should be rotated so that recess 269 in plate 261 would no longer be aligned with disc 216, reciprocation of shaft 248 lengthwise within bore 249 would be prohibited as plate 268 would abut disc 216. It-is thus-seen that reciprocation of shaft 248 is prevented unless sector member 264 and plate 261 thereto fastened is disposed in the particular angular position shown in Figure 8, with recess 269 aligned with disc 216.

However, with the parts disposed in the position shown in Figures 6 and 8,'shifter fork 28I is in its neutral position and His thus seen that shaft 248 may not be reciprocated to bring gear 245 into meshing engagement with gear rack 234 to cause actuation of the reverse shifter fork 226 to posimechanism just described therefore comprises an I tive reverse position unless shifter fork 28I is disposed in its neutral position. It is therefore impossible to shift the parts into reverse drive unless sliding clutch IN is in its neutral position.

It will further be appreciated that if shaft 248 and gear 249 are in meshing engagement with gear rack 234 to dispose reverse shifter 226 in reverse position, it will be impossible to reciprocate shaft. 248 in bore 249 until the reverse shifter fork 226 is brought into its neutral position. The

automatic and fool proof interlock for preventing both the forward and reverse shifter forks and sliding clutches from being disposed simultaneously in positive operative, position because of carelessness or inadvertence on the part of the vehicle operator.

rear extremity is supported in a bearing in amanner to be hereinafter disclosed. Shaft 385, to

- Automatic transmission and related mechanisms The enlarged portion I88 of shaft I46 is provided at its rear extremity with external teeth 3M, and is provided with a bore 382 in which is journalled, by means of bearings 383, the reduced end portion 384 of a shaft 385. Shaft 385 at its which is, spaced from needle bearings 383 by means of a ring 381. I

Disposed concentrically about the rear portio of shaft I46 and the forward portion of shaft 385 is a pinion carrier or cage member 389, the forward portion 3I8 of which is mounted for rotation about enlarged portion I88 of shaft I46 by means of roller bearings 3II. Bearings .3 provided with an outer race 312, are spaced from ball bearing assembly I85 by means of a bearing guard 3 I3, and are spaced from gear teeth 381 by means of a bearing guard 3. The rear'portion 3I1 of cage member 389 extends inwardly toward shaft 385 to form a hub, and an oil seal assembly 3I8 is secured to cage 389 and sealingly cooperates with shaft 385 to prevent lubricant from working therebetween and getting into the secondary clutch chamber. Seal 3I8 may be of any suitable form, and as it per se forms no part of the present invention, it will not be further described.

Cage member 389 isprovided with preferably two openings 322 in each of which is disposed a gear member 323 mounted for free rotation about a shaft 324 by means of a. bushing 325. Each shaft 324 is-secured at both its forward and rearward end within the cage member 389 with a ml teeth 338 which are adapted for meshing engagement with external teeth 38I formed on the rear end of shaft I46. Pinion 323 is further provided with external teeth 333 which are adapted to mesh with teeth 386 formed on the forward end of shaft 385. Lubrication of bushing members 325 is effected by means of an oil slot 335 formed in pinions 323.

Gears MI, 386, 33I, and 333 may be of the common spur variety of desired, but 1 preferably employ helical gears so as to promote quietness of operation. Although it is possible to design the gears so that the axial thrusts set up thereby completely balance each other, I preferably so design the gears that there is a slight unbalance of thrust applied to cage 388, because if the thrusts were completely balanced or neutralized", the assembly would possibly have a tendency to floatfiand produce noise.

Rotatably mounted in housing I28 by means 0 a bearing 3 and piloted on cage member 389 is a. cylindrical sleeve 343', which is secured to cage 344 is closely fltted'in a cylindrical housing or support 348, which is flanged as shown at 349. Flange 349 is piloted in a cylindrical recess 358 formed in transmission housing I28, and is secured to the latter in any suitable manner, as for example by cap screws 35I or the like. In order to prevent fluid leakage between flange 349 and housing I28, a gasket member 352 is preferably interposed therebetween. Collaror clutch race 344 is locked against rotation in its support. 348 by means of a plurality of keys which take the form of three pins 355 (Figure 3) disposed in recesses in the two parts. c

As seen in Figure 3, each roller 341 is urged in a counter-clockwise direction by means of a plunger 362, received within a cylindrical sleeve 363 accommodated in a bore 363 formed in collar member 3. Each plunger 362 is provided with a head 363 adapted to abut its corresponding roller 331. Each plunger and head is urged away from sleeve member 333, for urging each roller into engagement with its camming face, by means of a light compression spring 366.

The rear end of support 333 is provided with an oil seal assembly 356 which sealingly cooperates with the outer surface of sleeve 333 to prevent lubricant leakage between housing 333 and sleeve 333. Collar or clutch race 3, and the outer race of bearing 3, are respectively prevented from displacement in a forward direction by means of a snap ring 361 accommodated in a groove formed in housing 333. A shoulder 363 formed on sleeve 333 prevents rollers 331 from shifting forwardly. Collar 3 is prevented from displacement rearwardly by abutting contact with the ball bearing assembly 363, the outer race of which is adapted to abut a shoulder formed onhousing 333, and the inner race of which is adapted to abuta snap ring 353 accommodated in a groove in sleeve 333. ,Sleeve 333 is prevented from shifting rearwardly in bearing 3 by means of a snap ring 360 which is sprung into a groove located in sleeve 333 and engages the front face of bearing 33!.

From the structure thus far described, and with attention directed particularly to Figure 3 of the drawings, it will be appreciated that if sleeve 333, and cake or spider 303, which will be hereinafter collectively termed the carrier, tends to be rotated in a counter-clockwise direction with respect to collar 333, rollers 331 will be wedged between the exterior face of sleeve 333 and the camming face 336 of collar 3. Under such conditions, with the rollers wedged as just described, sleeve 333 is locked against counterclockwise rotation and such action occurs under certain special conditions of operation to be hereinafter disclosed in detail.

If, however,.sleeve 333 should tend to be rotated in a clockwise direction withrespect to collar 3, rollers 331 will tend to disengage themselves from camming surface 333 against the action of plungers 362 and will be urged out of wedging engagement between sleeve 333 and collar 333. Under such conditions sleeve 333 will be allowed to rotate freely in a clockwise direction with respect to collar 333, and such action occurs under normal operating conditions to be hereinafter described.

Since under normal operating conditions, sleeve 333 is rotated in a clockwise direction, and since the surface of sleeve 333 which is in contact with rollers 331 is cylindrical in configuration, it will beappreciated that no wear occurs between sleeve 333 and roller 331 under normal conditions of operation, as it has been found that a wedge of oil is formed in front-of each roller and substantially lifts it free and away from engagement with sleeve 333. This is made possibleby loeating the rollers in a stationary member, so that they will not manifest centrifugal forces. and by using comparatively light springs for actuating the rollers. This feature is of great importance and marks a distinct advance over prior overrunning clutches or free wheeling units, which under normal conditions of operation allow wear to take place between the free wheeling rollers and the rotating parts, with the result that their usefulness is greatly impaired.

Briefly, the operation of the torque multiplying mechanism is as follows: When rotational tendencies are transmitted through the primary clutch and the gear box to rotate shaft I46 in -a clockwise direction as viewed from the left of Figure l. pinion 301 formed on the rear end of shaft I36 tends to cause counter-clockwise rotation of planetary pinion 323, and, by means of gear 306 formed on the forward end of shaft 305,

to cause the planetary pinion to planetate rearwardly or counter-clockwise about gear 306, which is initially held stationary by the load. The resulting tendency of cage 309 to rotate in a counter-clockwise direction is prevented, however, by means of one-way clutch rollers 331 in the manner previously described.

Accordingly, counter-clockwise rotation of planetary pinion 323 therefore causes clockwise rotation of gear 306 and shaft 305. Torque is thus transmitted through the torque multiplying mechanism, and as gear 311i is of less diameter than gear 33i of the planetary pinion, and gear 333 of the planetary pinion is of less diameter than gear 306, it will be appreciated that torque transmitted from shaft 6 to shaft 305 in the manner just described undergoes a double ampliflcation.

After the load has been started and attains a predetermined speed under the influence of the torque multiplying drive just described, the transmission may be shifted to establish a direct drive between shafts I36 and 305, and the mechanism employed for effecting this result will now be described.

Secondary clutch mechanism Secured to the rear face ofsleeve 333, and mounted for rotation therewith in any suitable manner, as for example by bolts 310, is a web 3" of a flywheel-like member 312. Positioned within the flywheel and mounted concentrically about shaft 305 is a plate 313 which will hereinafter be termed the automatic plate.

Automatic plate 313 is adapted for rotation with flywheel 312 and forlongitudinal reclprocation therein by means of internal splines 383 formed on the flywheel and external splines 334 formed on the automatic plate, which mesh therewith.

Threaded into self-locking engagement in plate 313 as indicated at 313, and extending outwardly through openings 316 in the web of the flywheel and through disk plates 316 covering openings 316 is a plurality of bolts 311 which will hereinafter be termed holdback bolts". Each holdback bolt 311 is provided with a head 313 against which bears a compression spring 313 that encircles bolt 31] and the other end of which bears against plate 316 previously described. The holdback bolt assemblies are preferably symmetrically disposed in pairs about the periphery of plate 313 and in the present instance, six may be employed. It will thus be appreciated that automatic plate 313 is at all times urged toward the flywheel web by means of springs 313.

Mounted upon a splined portion 335 of shaft 333 is a hub 331 provided with a flange 333 to which is secured in any suitable manner as foremployed with driven disc 14 of the clutch.

Facing 391 is adapted to cooperate with the rear face of automatic plate 313, and facing 392 is adapted to cooperate with the .front face of a plate 393 which will be hereinafter termed the floating plate.

'Ihe floating plate is adapted for rotation with flywheel 312 and for reciprocation therein by means of external splines 394 formed on the floating plate which cooperate with the internal splines 393 formed on the flywheel as previously described.

A cover member 396 is located at the rear face of flywheel 312 and is secured theretoin any suitable manner, as for example by means of bolts 391 or the like. Through apertures 399 formed in cover 396 extend a plurality of bolts 399, each of which is provided with a reduced portion 491 which is threaded into self-locking engagement with floating plate 393. 'Bolts 399 may be equal in number to and disposed in opposite relation to bolts 311 threaded in the automaticplate, six bolts thus being employed. Each bolt 399 is provided with an enlarged head 492 which is primary greater in diameter than the aperture 399- in the cover member, and bolt 399 is in consequence prevented from lateral displacement further to" the left of its position as seen in Figure 1, by virtue of the abutting relation existing between heads 492 of the bolts and cover plate 396. A plurality of washer-like shims 493 are preferably disposed between the heads of bolts 399 and cover 396 for adjustment purposes. Disposed between the floating plate 393 and the cover member 396 are a plurality of compression springs 495 adapted at one end to be received within recesses 496 formed in the floating. plate, and at their other end adapted to be received in recesses 491 formed in the cover member. Springs, 495'are preferably six in number and may be symmetrically disposed in pairs about the peripheryof the float- From the structure thus far described, it will be appreciated that automatic plate 313 and the web-portion 311 of the flywheel are at all timesurged together by means of compression spring 319 in the manner previously described. It will further be appreciated that floating plate 393 is at all times designed to be urged away from cover member 396 by virtue of the action of compression springs 495. With the engine dead or idling at very low speeds, the parts may be disposed in the position disclosed in Figure 1, and under such circumstances, driven disc 399 has no torque transmitted to it through either the automatic plate 313 or the floating plate 393,-by virtue of the fact that aclearance exists between facing 391 and the automaticsplate 313. This clearance corresponds substantially to the idle release clearance of the primary clutch, previously described.

The automatic plate may be urged away from web portion 311 of the flywheel in any suitable manner to produce clutch engagement, but on the present embodiment of my invention it preferably takes the form of a centrifugally operable mechanism similar to that disclosed in connection with the primary clutch, and as the centrifugal mechanism of the secondary clutch is similar to the centrifugal mechanism previously described in connection with the primary clutch, only brief description thereof will be made.

Preferably three weight levers 4| 1 provided with other ends carry weight assemblies 416 secured thereto by means of nuts 411 or the like. The face of each head 412, remote from the bottom of recess 414, is indicated at 419 and reacts against the web of the flywheel. With the flywheel operating at or below a predetermined speed,- the force exerted by compression springs 319 will be ample v to prevent movement of the automaticplate 313 away from the web 311 of'the flywheel. Under these conditions, heads 412 of the centrifugal weight assemblies will be held in the position shown in Figure 1, and a clearance will exist between automatic plate 313 and the driven disc 399, and also between plate 393 and the driven disc clearance may exist.

The rear end of shaft 395 is supported in the ball bearing assembly 421 supported in a cover member 422 secured to the rear end of transmission housing 129 by cap screws 423 or the like. Bearing assembly ,421 is retained in position with respect to housing 422 by means of a split ring 424. The inner race of the bearing assembly is maintained in position on the splined portion 395 of shaft 395 by means of a split ring 425. Also splined upon shaft 395 is a worm gear 421 adaptedto drive a pinion gear 423 connected with the speedometer mechanism to indicate the speeds at which the vehicle is travelling. Lubrication of speedometer mechanism 429 and ball bearing 421 is effected by means of a grease fitting 429 connected into cover member 422.

Shaft 395 may be connected to the driven load in any suitable manner, but in the present instance a sleeve 439,-provlded with a flange 431 is splined upon shaft 395 and is adapted to be secured to the forward universal joint of an automotive vehicle in any suitable manner. Sleeve 439 is retained upon driven shaft 395 by means of a nut 432 threaded upon the end of shaft 395 and retained in adjusted position by means of a cotter pin indicated at 434. Nut 432 forces sleeve 439, gear 421 and bearing 421 to the left and brings the inner race of bearing 421 into tight engagement with split ring 425. Shaft 395 is accordingly positively fixed against axial displacement in bearing 421, and certain An oil seal assembly 435 is disposed between cover member 422 and sleeve 439 for the purpose of preventing leakage of oil therebetween.

Integrallyformed upon rearcover 422- is an apertured lug 436 which is adapted to be secured to a vehicle frame member for supporting the transmission in operative relation to the vehicle.

The operation of the secondary clutch mecha-.

nism is briefly as follows: Should the rotational speed of the flywheel exceed a predetermined value, masses 419 will be centrifugally thrown out wardly with the result that levers 411 pivot about knifecdges 413 and cause reaction face 419 of each centrifugal head to fulcrum against the web of the flywheel. In this manner, automatic plate 313 is urged away from the web of the flywheel,

- and as rotational speed of the secondary clutch is increased, weights 6 wfll swing further outward, automatic plate 313 being displaced further away from the flywheel web until it comes into engagement withfacing 39I of the driven disk 393. Upon further increase of the rotational speed of the secondary clutch, masses 6 will swing still further outwardly and automatic plate 313 which is now in engagement with driven disc 393, will urge the latter toward the rear of the clutch until face 392 thereof is in engagement with the floating plate 393.

As the weights 6 swing still further away from shaft 335 into their maximum outward position, automatic plate 313, driven disk 393 and floating plate 393 will together be urged toward cover 394 of the flywheel against the action of compression spring 435. Pressure is thus built up between the plates, and the automatic plate, the driven disc and the floating plate are brought into synchronism without shock.

Since the web of the flywheel is rigidly bolted to the carrier, and since driven disc 393 is splined to rotate with shaft 335 when the automatic plate and the driven disc attain the same angular velocity, cage member 339 and shaft 335 will also be rotating at the same angular speed. Pinion shaft 324, carried by.cage member 339, will then revolve about the axis of shaft 335 with the same angular speed with which shaft 335 is rotating about its own axis. When such motion of pinion shaft 324 and shaft 335 is eventuating, it will be appreciated that there can be no rotation of pinion gear 323, as pinion shaft 324, pinion 323 and gear 336 will under such circumstances be rotating as a unit. As a result, teeth 33I on pinion 323 and teeth 33I on shaft I46 act merely to key shaft I46 to the pinion gear and cage unit. It will therefore be readily appreciated that shaft I46 and shaft 335 under such conditions will be rotating at the same angular speed due to the fact that shaft I46, pinion 323, pinion shaft 324 and shaft 335 rotate as a unit at a common angular speed.

The operation just described will occur when the secondary clutch is engaged and a condition of direct drive will exist from shaft I46 to shaft 335 If, however, the parts are disposed in the position in'Flgure 1 with the secondary clutch disengaged, torque will be transmitted to shaft I46 and shaft 335 through the torque multiplying mechanism including pinion 323 in the manner previously described.

Pinion carrier lock mechanism Under conditions of reverse drive, to be hereinafter described, it becomes desirable and necessary to lock cage member 339, together with the secondary clutch, against rotation. Such result is accomplished by means of the structure about to be described.

Shrunk upon-theforward portion of member 339 is a gear ring I provided with teeth 442.

.Adapted for cooperation with teeth 442 is a de- Referring to Figurefl, it will be seen that with the parts disposed in the position therein disclosed, portion 454 and offset 448 are not in registry. However, upon lateral shifting of reverse shaft 229 to the left as seen in Figure 7, portion 454 thereof will be brought into registry with offset 448 to allow -the latter to be received in portion 454 and allow counter-clockwise rotation of shaft 444 as seen in Figure 4, to bring detent 443 into engagement with teeth 442 formed on the planetary carrier member.

With offset 448 received in depression 454 of shaft 229 and with planetary carrier 3I3 locked against rotation in a clockwise direction as seen in Figure 4, release of carrier 3I3 may be effected by reciprocation of shaft 229 to the right to move depression 454 out of registry with offset 448 and cause clockwis'e rotation of lever 444 to bring detent 443 out of engagement with teeth 442. It will therefore be readily seen that locking and unlocking of carrier member 3I3 is effected by a lateral shifting of reverse shifter shaft 229.

Such reciprocation of reverse shifter shaft 229 is effected as previously described by reciprocation of gear rack 234 to cause movement of the reverse idler gear into or out of its operative position. When shifter shaft 229 is moved to the left as seen-in Figure '7, the reverse idler gear is brought into meshed engagement with teeth I13 and I82 to cause positive reverse drive of shaft 335 with respect to shaft I46. Such recip= rocation of shaft 229 is simultaneously effective to bring depression 454 thereof into registry with offset 448 and allow detent 443 to mesh with teeth 442 formed on the pinion carrier and thereby lock said carrier against rotation. It will thus be seen that by means of the structure just described, planetary carrier 339 is automatically locked against forward rotation when the idler reverse gear is brought into positive operative position, and the planetary carrier 339 is unlocked and allowed to rotate automatically upon ,mo'vement of the reverse idler gear into its neutral position; This result is essential to the proper transmission of reverse torque to be hereinafter described.

Before proceeding to a description of the operation of my device, I will briefly describe the action of the gears used in the gear box and transmission. The gears employed in these units may assume any suitable form, but I preferably use helical gears to promote quietness of operation, and as constant mesh gear boxes are well known in the art, the action of the gear box gears will be readily understood without further discussion.

With reference to the transmission, gears 33I and 333 are of opposite pitch and are desi ned so that when they are transmitting power from the engine to the load, the thrust tends to force gears 33I and 336 axially apart, and when the vehicle tends to drive the engine these gears tend to be brought toward each other. The two directional axial thrust applied to gear "I as a result provided, they can efliciently handle axial loads of considerable magnitude and they can accordingly adequately handle the thrusts imposed thereupon by the gears. I

As previously explained, the thrusts of the gears are only partially neutralized, with the result that an unbalanced'thrust of low magnitude is applied to carrier 309 through thrust washers 321 and 328. The direction of this thrust depends upon the direction of the drive, but it is completely resisted, irrespective of-its direction, by bearing 3, whichrestrains carrier 309 against axial movement in either direction.

When the device is placed in operation, both the gear box and the transmission chambers are supplied with lubricant of suitable grade, and it is allowed to'circulate from one chamber to the other through suitable openings in partition I66 (not shown) v General operation The operation of the mechanism thus far described will now be set forth in detail. Assuming that the parts of the mechanism are disposed in the positions which they will occupy under starting conditions, forward drive sliding clutch I6I and reverse drive sliding clutch 222 of the gear box will be disposed in neutral position as shown in Figure 1. If the engine is now startedand operated at a predetermined speed, for example at a speed corresponding substantially to the idling speed of the prime mover utilized therewith; there will be no driving connection betweenshafts 3 and 9, as the primary clutch will be disengaged as illustrated in Figure 1.

The prime mover may now be warmed up and the driving shaft 3 operated at a speed substan tially above idling speed, and although the primary clutch under these conditions will engage,

and power will be transmitted from shaft 3 to shaft 9, there will be no transmission of power between shaft 9 and shaft I46 due to the fact that both sliding clutch I6I and reverse sliding clutch 222 in the forward gear box are disposed in their neutral positions, as previously described.

If desired, while warming up the prime. mover, the primary clutch may be manually disengaged to prevent transmission of torque to shaft 9 by depressing clutch pedal II. V

Low speedutorque multiplying drive If, under normal conditions it is now desired to start the vehicle in motion, the dash controlis manipulated to cause reciprocation of sliding clutch I6I to the left as seen in Figure 1 into its high position ,until teeth I64 thereon are in engagement with teeth I43 of the rear end of shaft 9', and the engine is accelerated. By normal conditions I mean with the vehicle located on a substantially level, hard surface.

As the driving shaft is accelerated, the centrifugal weights of the primary clutch fulcrum outwardly in response to centrifugal force and cause the primary clutch mechanism to be engaged in the manner previously described, thereby coupling shafts 3 and 6. 7

Transmission of torque from shaft 0 to shaft I46 is effected through the medium of internal teeth I 43 on pinion I4I formed on the rear end of shaft 0 which teeth are in meshing engagement with external teeth I64 formed with collar I6I. By virtue of the fact thatcollar I6I is splined to rotate with shaft I46, clockwise rotation of pinion I, as viewed; from the left of Figure 1, is effective through teeth I43 and I64 and spline I6I, to cause rotation of shaft I46 in a clockwise direction and torque is thus transmitted from shaft 0 to shaft I46.

Simultaneously with such operation, pinion I on shaft 6 tends to produce; counter-clockwise rotation of gear I66 in the forward gear box by virtue of the fact that shaft "I16 onwhich gear I66 rotates is rigidly supported in the transmission housing. Gear I60 is in meshing engagement with gear I63 which is freely rotatable upon shaft I46, and gear I63 is therefore rotated in a clockwise direction freely upon shaft I46.

Thus under normal starting c'onditions'with the gear box conditioned for direct drive, torque .will be transmitted directly and without ampli flcation from shaft 6 to shaft I46.

If, however, it is desired to put the vehicle in motion under conditions which are other than normal, as for example upon a steep grade or with an unusually heavy load, sliding clutch I6I may be reciprocated to the right as seen in Figure linto its low" position until teeth I66 thereof are in engagement with teeth I56 formed on gear I63. As previously explained, such reciprocation of sliding clutch I6I may be effected by means of the dash control assembly described in connection with Figures 6 and B of the drawings.

With the parts disposed-in this position, clockwise rotative tendencies of shaft 9 as viewed from the left hand end of Figure 1 are, in the manner just described, effective by means of pinion I and countershaft gear I69 to cause pinion I53 to rotate in a clockwise direction. By fvirtue of v the fact that gear I63 and sliding clutch I6I are now keyed, together through the medium of teeth I66 and I66 and that sliding clutch I6I is further splined to rotate with shaft I46, it will be appreciated that rotation of gear I63 in the clockwise direction just described will be effective to cause rotation of shaft I46 in a clockwise direction, and torque will therefore be transmitted load imposed thereon whenplanetary gee-r323 tends to rotate in a counter-clockwise direction,-

it tends to planetate about gear 306 and carry its shaft 324 and cage member 309 therewith. Counter-clockwise rotation of cage member 309 and planetary shaft 324 thereby carried, however, is prevented by the overrunning clutch.

Any counter-clockwise rotation of planetary gear 323 about its shaft within the locked cage 300 is therefore effective to cause clockwise rota- As pinion 323 is also con- 

